Cutter chain having increased conveying ability

ABSTRACT

A cutter chain and support means therefor and more particularly a mining apparatus cutter chain having a plurality of lug portions integral with links of such a cutter chain for substantially increasing the conveying ability of the chain over the natural conveying ability thereof.

United States Patent 1 Rollins sl l 3,724,901

45| Apr. 3, I973 [54] CUTTER CHAIN HAVING INCREASED CONVEYING ABILITY[76] Inventor: Lester G. Rollins, 650 Forest Lane,

Franklin, Pa. 16323 221 Filed: June 2,1971

[21] Appl. No.: 149,263

Related US. Application Data [63] Continuation-impart of Ser. No.786,649, June 24,

1968, abandoned.

[52] US. Cl ..299/84, 299/67 [51] Int. Cl. ..E2lc 25/34, E210 35/20 [58]Field of Search ..299/67, 82-84 [56] References Cited UNITED sTATEsPATENTS 7 1,410,503 3/1922 Porter ..299/67 Joy ..299 s3 Joy ..299 83Primary Examiner-Ernest R. Purser Attorney-E. Wallace Breisch [57]ABSTRACT A cutter chain and support means therefor and more particularlya mining apparatus cutter chain having a plurality of lug portionsintegral with links of such a cutter. chain for substantially increasingthe conveying ability of the chain over the natural conveying abilitythereof.

10 Claims, 9 Drawing Figures PATENTEUAPRB 1m 3,724,901 I SHEET 1 OF 3 avVEN r'on LESTER 6. ROLL/NS PATENTEDAPR 3 I975 sum 3 BF 3 D D Qmw sum mumw INVENTOR. LESTER 6. ROLL/NS CUTTER CHAIN HAVING INCREASED CONVEYINGABILITY This application is a continuation-in-part of my copendingapplication Ser. No. 786,649 filed June 24, I968 and now abandoned.

In a mining apparatus which incorporates the principles of thisinvention a disintegrating head mechanism is used to dislodge mineralfrom amine vein and is operable to provide mine passageway or room intowhich the apparatus advances as mining progresses. The disintegratinghead mechanism is. pivotally mounted on a mobile base to swing in avertical plane between the mine roof and floor and includes a rotarydrum cutting head assembly which comprises end portions and a centrallylocated cutter chain spaced between such end' portions. The apparatusalso ineludes a conventional loading head for gathering the loosemineral on the mine floor and moving it rearwardly and inwardly towardthe forward receiving portion of the conveying means of the apparatus.

The present invention contemplates improvement of such known type ofmining apparatus, for examplez-an improved cutter chain aids in removingdislodged mineral from the face shelf during the sumping and shearingphase of a mining operation; and an improved cutter chain drive sprocketstructure for superior supporting of the cutter chain.

These and other objects and advantages of this invention will becomemore readily apparent from the following description and drawings inwhich:

FIG. 1 is a perspective view partially schematic of a mining machineembodying the principles of this invention;

FIG. 2 is an enlarged view, partly in section, taken on line 2-2 of FIG.1 and showing the cutter head assembly;

FIG. 3 is an enlarged side view of an alternative cutter chain drivesprocket structure of this invention;

7 FIG. 4 is an enlarged view, partly in section, taken on line 4-4 ofFIG. 3;

FIG. 5 is an enlarged plan view of a portion of the cutter chain of thisinvention;

FIG. '6 is a side view of the portion of the cutter chain illustrated inFIG. 1;

FIG. 7 is a cross-sectional view taken on line 7-7 of FIG. 5;

FIG. 8 is a cross-sectional view taken on line 88 of FIG. 5; and

FIG. 9 is a partial schematic plan view of a portion of anotherembodiment of a cutter chain embodying the principlesof this invention.

A continuous mining machine, generally designated at 10, which embodiesthe principles of this invention may assume various forms but forillustrative purposes,

herein comprises a crawler base 14 carrying a frame 16 on which aforwardly extending mining boom 18 is pivotally mounted at the forwardend of frame 16 to swing up and down between a mine roof'and a minefloor. A cutting head assembly 24 extends transversely of boom 18 and isrotatably secured thereto at the forward end thereoffPivotally mountedat the forward end of frame 16 and extending forwardly therefrom beneaththe boom 18 is a conventional loading head 26 having oscillatorygathering arms 28 for engaging mined mineral and moving such mineralrearwardly and inwardly toward a well known conveying means'30 of themining machine 10. Conventional fluid jacks (not shown) serve to swingthe boom 18 in a vertical plane about the pivot axis thereof and tiltthe loading head 26 about the horizontal axis thereof. The fluid 5 jackshave one end thereof secured to the forward end of frame 16 and have theother end thereof secured to I respective rearward lever ends of boom 18and loading head 26. Motors 36, which are suitable rigidly secured bybrackets 38 to boom 18, drive the cutting head assembly 24 in anysuitable manner.

As shown in FIG. 2, the cutting head assembly 24, which is rotatablydriven by any suitable gearing arrangement, for example, that gearingarrangement shown and illustrated in U. S. Pat. application No. 786,650,filed Dec. 3, l968, and assigned to the same assignee as is thisinvention, comprises: an endless circulating belt type continuous hingecutter chain 76 which is symmetrical with respect to the center line ofmachine 10; hollow cylindrical rotary drum cutting heads 78 which extendoutwardly from respective sides of chain 76; and hollow cylindricalrotary drum cutting head extensions 80 which are slidably partiallyreceived within respective heads 78 and are selectively hydraulicallyextendable outwardly therefrom. A cutting head assembly drive shaftwhich is rotatably supported by a forward portion 74 of a gear casing 56located at the forward end of boom 18, extends transversely throughheads 78 and extensions 80 and rotatably drives the cutting headassembly 24. For a more detailed description of the structure andoperation of cutting head assembly 24 and shaft 70 reference is made tothe hereinabove mentioned U. S. application Ser. No. 786,650.

At the longitudinal centerline of machine 10 a cutter chain drivesprocket 82 is in splined engagement with shaft 70. Drive sprocket 82has a plurality of teeth 84 around the outer periphery thereof whichdrivably engage the cutter chain 76 as hereinafter described. A suitablerear idler sprocket 86 which is rotatable on a shaft 88 which extendstransversely of the boom 18 provides well known tensioning and motionreversing means for the cutter chain 76 to form a continuous orbitalpath therefor. f

Each rotary drum cutting head 78 has a radially outwardly extendingflange 106 at the inner ends thereof and a reduced diameter portionthereof forms a chain end supporting seat 108 which extends axially fromflange 106 toward the center line of machine 10. Seats 108 extend undera portion of the outer edges of the endless circulating cutter chain 76and with such a location act to support the bight portion of the cutterchain 76 at the edges thereof where it is trained about the rotary drumcutting heads 78. The relative rotational speeds of the cutter chain 76and the seats 108 are equal and therefore there is no movement of cutterchain 76 with respect to the seats 108 during the time chain 76 issupported by seats 108. Because of this lack of relative movement thereis no wearing between the respective contact surfaces of seats 108 andchain 76.

The cutter chain drive sprocket 82 is dimensioned to provide a rootsurfaces 110 thereof which lies in approximately the same cylindricalsurface as the contact surfaces of the spaced seats 108. With such rootsurfaces ll0, each link in the bight portion of chain 76 is supported atthree areas namely; end supports at the contact surfaces of the spacedseats 108; and a central support at the root surface 110 of the drivesprocket 82. With such a support arrangement deflection of chain 76 isminimized and the maximum bending moment due to cutting loads is reducedover that deflection and bending moment which would develop under thesame loading if the chain 76 had only one or two areas of support.

This support arrangement allows the use of cutter chains having agreater chain width to pitch length ratio than previously permitted, forexample a chain width to pitch length ratio of four to one, or more. Awidth to pitch length ratio of no less than four to one is necessary forthe construction of a chain width large enough for thepurposes of thisinvention as hereinafter set forth while maintaining a sufficientflexibility to avoid unreasonably large sprocket diameters. If the chainwidth to pitch length ratio is less than four to one, the required chain.width would yield a pitch length requiring sprockets too large to beused in a cutter head such as hereinbefore described. The above chainsupporting arrangement is fully illustrated and shown in thehereinbefore mentioned U. S. application Ser. No. 786,650.

An alternative cutter chain central support area constructed accordingto the principles of this invention is shown in FIGS. 3 and 4 andcomprises a cutter chain drive sprocket 82 having spaced shoulders 109thereon at the flanks of teeth 84'. There are no shoulders 109 at thetooth root 110 and the shoulders 109 areso dimensioned that the diameterof the shoulder circles is substantially greater than the diameter ofthe tooth root circle. With such an arrangement as illustrated in FIGS.3 and 4, each link in the bight portion of chain 76 is supported at fourareas namely; end supports at the contact surfaces of the spacedshoulders 109. With such a four area support arrangement the advantagesof the hereinbefore discussed three area support are maintained,however, thefour area support arrangement has additional advantages suchas superior wearing ability and reduced breakage compared to the wearingand breakage tendencies present with a three area support arrangement.

Well known screw type continuous conveyor scrolls 118 are secured to theouter periphery of rotary drum cutting heads 78 and to well knownsupporting sheaths 115 which are secured to the outer end portions ofthe rotary drum cutting head extensions 80 which is not selectivelyreceivable within cutting head 78. Such sheaths 11S allow the extensionand retraction of head extensions 80 while still maintaining asubstantially continuous conveying scroll 118 with respect to the scroll118 on heads 78. Scrolls 118 and the cutting chain 76 have a pluralityof suitable bit holders 120 secured adjacent the outer peripheral edgesthereof in a suitable spaced orientation to one another. A cutter bit122 is inserted in each bit holder 120. Cutter bits 122 may be of anysuitable type and as shown are plumb bob deep penetrating point attackconical bits. The scrolls 118 are suitably arranged to convey a portionof mineral mined by bits 122 inwardly from such bit location toward thecutting chain 76. End cutter caps 124 are suitably secured to the outerends of head extensions 80. Bit holders 120 and cutter bits 122 aresecured to caps 124 in a suitable spaced orientation to one another.

Referring to FIGS. 5 through 8 the cutter chain 76 comprises a pluralityof links 200 which are hingedly connected by means of a continuous hingegenerally designated at 202. Hinges 202 are elongated transversely ofcutter chain 76 between adjacent links 200 and comprise interfittinghinge portions as hereinafter described in detail which make up asubstantially continuous bore 204 through the respective hinges 202 forinsertion of elongated cylindrical hinge pins 206 therein.

Each link 200 comprises an elongated plate or body portion 208 having aplurality of elongated partially cylindrical hinge portions axiallyspaced along the sides thereof. For purposes of description theuppermost side surface of the body portion 208 as viewed in FIG. 5 isdesignated 214 and the lowermost side surface thereof is designated 216.In addition, inward and outward as used hereinafter shall refer,respectively, to toward and away from the centerline of machine 10.

The hinge portions of links 200 are formed integrally with the bodyportion 208 or rigidly secured thereto as by welding or the like. Side214 includes hinge portions 218, 22 0 and 222 extending therealong suchthat: portions 218 have the outer ends thereof in transverse alignmentwith the two outer ends of main body 208; portions 220 are spacedinwardly from portions 218 respectively a distance slightly greater thanthe axial length of portion 218; and portions 222 are similarly spacedinwardly from respective portions 220. Sides 216 include hinge portions224, 226 and 228 extending therealong such that: portions 224 are spacedinwardly from the two outer ends of body portion 208 a distance slightlygreater than the axial length of portions 218; portions 226 are spacedinwardly from portions 224 a distance slightly greater than the axiallength of portions 220; and a longer center portion 228 is symmetricalwith respect to the centerline of cutter chain 76 and has the axialendsthereof spaced from adjacent portions 226 a distance slightlygreater than the axial length of portions 222. The axial length andcross-sectional configuration of portions 218-222, 224 and 226 I aresubstantially equal. The cross-sectional configuration of portions 228is substantially equivalent to the portions hereinabove mentioned andthe axial length thereof is greater than the axial length of suchportions.

With such an arrangement, as hereinbefore described, of hinge portions218-228 along respective sides 214 and 216, a continuous hinge 202 canbe formed by aligning the side 216 of an upper link 200 with the side214 of. a lower adjacent link 200. The position of hinge portions onsides 214 and 216 of adjacent links 200 are spaced as previouslydescribed to allow the respective hinge portions of the upper link 200to be received in the spaces between the hinge portions of the lowerlink 200. After such aligning and receiving'of respective hinge portionswithin the spaces between hinge portions of adjacent links 200, thehinge pin 206 is inserted within the substantially continuous bore 204.Pins 206 are confined within bores 204 by any suitable means, forexample keeper pins 231 positioned in bores 204 inwardly adjacent theouter end of link 200.

A centrally located drive sprocket opening 230 is provided in bodyportion 208 through which a tooth 84 of cutter chain drive sprocket 82extends to drive the cutter chain 76. Openings 230 may be of anysuitable configuration which will permit suitable tooth engagement todrive chain 76. As shown opening 230 is a generally square openingsymmetrically located with respect to the centerline of machine 10. Thedistance between centerlines of links 200 sometimes referred to as thepitch of the chain equals the pitch distance of the teeth 84 of drivesprocket 82.

Cutter chain 76 has a plurality of suitable bit holders 120 (only one ofwhich is shown in FIG. 5) secured thereto in any suitable manner,-forexample welding around the peripheral edges of a bit holder l20to joinsuch holder to body portion 208. A cutter bit 122 is inserted in eachbit holder 120. The bit holders are positioned in a suitable spacedorientation to one another to mine mineral forwardly of machine and assuch there is no requisite that each and every link 200 have a bitholder 120 thereon.

Cutter chain 76 additionally includes a plurality of conveyor flightsgenerally indicated at 232 (only one of which is shown in FIG. 5) whichextend transversely of cutter chain 76 between adjacent links 200.Flights 232 are formed from a plurality of aligned lug portions whichproject upwardly (to the left in FIGS. 6-8) from the working surface ofchain 76.

Such lug portions are formed integrally with hinge portions 218-228 orare rigidly secured thereto as by welding or the like and include; lugs234 which extend along substantially the entire length of hinge portions218 and 220 and project upwardly from the side of such portions 218 and220 which is nearer to the body portion 208; lugs 236 which extend alongsubstantially the entire length of hinge portions 224 and 226 andproject upwardly from the side of such hinge portions 224 and 226 whichare farther from the body portion 208; lug 238 which extends alongsubstantially the entire length of hinge portion 228 and projectsupwardly from the side of hinge portion 228 which is nearer to the bodyportion 208; and lugs 240 which extends along substantially the entirelength of hinge portions 222 and the length intermediate such portions222. Each lug 240 has the outer ends thereof projecting upwardly fromthe sides of hinge portions 222 which are nearer the body portion 208and a portion 242 thereof intermediate the outer ends projectingupwardly from the side 214 of body portion 208. Such portion 242 has theside thereof which is further from body portion 208 concaved radiallyinwardly at a radius substantially equal to the radius of hinge portion228. Such a concaved surface of portion 242 cooperates with hingeportion 228 to facilitate the flexibility of cutter chain 76.

Upon assembly of adjacent links 200 in a manner hereinbefore described,lug portions 234 to 240 form conveyor flights 232 which are in spacedrelationship to one another to define conveying pockets 233 in cutterchain 76 between adjacent flights 232.

To mine mineral from a mineral face, the operator of machine 10initially pivots the boom 18 upwardly to a mine roof line. After suchinitial pivoting the cutter head assembly 24 is sumped forwardly tobegin a cut in the mine face. After the sumping is completed the boom 18is drawn downwardly toward the mine floor until the shear cut of theface is complete. During the sumping and shearing phase it is importantthat the mined mineral be quickly removed from the face ledge (Le, thetransverse shelf area which exists between the old forward face and thenewly mined 'forward face until the shear cut is complete upon whicharea the main mining action occurs). If the mineral is not quicklyremoved the efficiency of the cutter head assembly 24 is greatly reducedbecause of increased horsepower demandand slower cutting rate and,additionally, an inordinate'amount of undesirable mineral fines isproduced.

To insure the removal of the mined mineral from the ledge and conveyingsuch mineral away from the face, the conveying flights 232 must beconstructed to a specific heighth. .The depth of the flights 232 (Le,that distance from the top of flights 232 down to the upper or workingsurface of body plate 208) determines the conveying capacity of thecutter chain 76. In other words the depth of the flight 232 times thewidth of the chain 76 times the pitch of the sprocket 82 (Le, the

width of a link 200) determines the maximum volume of mineral which canbe conveyed off the shelf by any one link 200. Such a flight depth isarrived at by analytical means which consider: the type of cutter bit122 used; the operating speed of the cutter head assembly 24; themaximum and minimum volume of mineral which will be dislodged by thecutter chain 76 during a given increment of time at various shear andsump speeds and with the use of different type bits 122; the pattern ofbits 122 on the cutter chain 76; and the like. After an evaluation ofthe above factors an optimum arrangement of elements is decided upon andthis arrangement plus the maximum usable operating speed decides themaximum volume of mineral which can be mined by the cutter chain 76during a give increment of time. This maximum loose volume of minedmineral therefore determines the depth of the flights 232 for theflights must be capable of conveying at least this volume off the shelfin the same given increment of time, for example; a cutter chain 76having a kerf width of 30 inches and operating at a shear speed of 1inch per second on a 30 inch ledge will mine 900 cubic inches of mineralper second, therefore, the flights 232 must be so dimensioned as todevelop a conveying capacity for chain 76 of at least 1,800 cubic inchper second (1,800 cubic inches is arrived at by doubling 900 cubicinches because the loose mineral volume is approximately twice the solidmineral volume). Chain 76 conveying capacity (cubic inches per second)is defined by the rate of chain travel (inches per second) times thewidth of chain 76 (inches) times the depth of a flight 232 (inches).

It is to be understood that all cutter chains have a natural conveyingcapacity without the presence of conveying elements thereon. Such anatural conveying capacity occurs because of: the physical relationshipbetween the cutter chain and the shelf giving rise to a frictional forcewhich develops on the mined mineral therebetween; and the frontal areaof the cutter bits and bit holders convey mined mineral in the immediatevicinity thereof. Such a natural conveying capacity is ofteninsufficient to insure the removal of mined mineral from the ledge andconveying of such mineral away from the face. In addition, if pointattack conical bits are used as the cutting elements of a mining machinethe use of conveying flights 232 is even more necessary for theefficient operation of the mining machine for such bits have asubstantially larger cutting capacity in relation to their frontal area.

Preferred embodiments of this invention having been hereinbeforedescribed and herewith illustrated it is to be realized that variationsin the specific structure are envisioned and contemplated, such as:flights 232 can comprise lugs which are common to more than onehinge-portion; the lugs do not necessarily have to be in alignmentacross the width of cutter chain 76, but can be staggered and still,perform substantially the same function as if they were aligned; thelugs can extend upwardly from the body plate 208 rather than upwardlyfrom the hinge portions as is hereinbefore described; and the four areasof support for the bight portion of chain 76 can deviate from a commoncylindrical surface by a substantial misalignment but not sufficient toresult in stressing a link beyond the yield point thereof.

One of the variations discussed hereinabove is shown in FIG. 9 whichschematically illustrates a portion of cutter chain 76' similar to thecutter chain 76 described hereinbefore with the primary distinctiontherebetweenv being that the flights 232' thereof are chevron shaped andare formed from staggered lugs 250 which project upwardly from-the bodyof the links 200'. As shown lugs 250 are located such that each flight232{ extends the length of two adjacent links 200 and the staggering andlength of the lugs 250 on adjacent links provides for flights 232extending substantially continuously across the width of the cutterchain 76. A pair of adjacent flights 232 define conveying pockets 233'therebetween for conveying removed mineral away from the mine face. Asshown, the width of conveying pocket 233' at any point therealong issubstantially equal to the distance between adjacent hinges of chain 76;I

Preferred embodiments of this invention having been hereinbeforedescribed and herewith illustrated it is to be realized that variationsin the specific structure are envisioned and contemplated withoutdeparting from the scope of the invention, for example: flights can bearranged in manners other than as described hereinbefore; the lugs canextend upwardly from the body plate rather than upwardly from the hingeportions as is hereinbefore described; and the four areas of support forthe bight portion of chain 76 can deviate from a common cylindricalsurface by a substantial misalignment but not sufficient to result instressing a link beyond the yield point thereof.

It is. therefore respectfully requested that this invention beinterpreted-as broadly as possible and limited only by the scope of theappended claims.

What is claimed is:

l. A cutting chain comprising, a plurality of chain sections pivotallyconnected by parallel hinge pins to form a continuous chain of adjacentones of said sections, having a transverse width to pitch length ratiogreater than four to one, bit blocks carried by at least some of saidsections; and said sections having material receiving portions forconveying material cut during movement of said continuous chain in abedded deposit of material.

2 A cutting chain as specified in claim 1 wherein said conveying is at arategreater than the loose volume rate of mineral production by saidmovement of said chain sections in a bedded deposit of mineral.

A cutting chain as specified in claim 1 wherein each of said chainsections connects two of said pins at a plurality of points spacedlongitudinally of said ,pins and each of said pins extends the fullwidth of said chain.

4. A cutting chain as specified in claim 1 wherein.

each of said chain sections has a plurality of conveying means spacedalong said hinge pins to form said material receiving portions.

5. A cutting chain as specified in claim 4 wherein at least some of saidbit blocks extend upwardly from said body portion and the height of saidconveying means less than the height of said bit blocks.

6. In a cutting chain as specified in claim 4 the further improvementwherein said conveying means are located on interfitting portions ofsubstantially continuous hinges.

7. An endless cutting chain comprising: a plurality of links, each ofsaid links including a body portion having a transverse width greaterthan the length thereof, each of said body portions being hingedlyconnected to adjacent ones of said body portions along axes extending inthe direction of said width, respectively; bit blocks carried by atleast some of said links; each of said links having a plurality ofmembers extending upwardly from said body portion and in said directionof said width, said members on a plurality of said links formingconveyor means extending substantially continuously in said direction ofsaid width, respectively, and adjacent pairs of said conveyor meansspaced laterally from each other to form material receiving portions ofa volume to convey material cut during orbital movement of said links ina bedded deposit of material.

8. An endless cutting chain as specified in claim 7 wherein adjacentlinks have a width to pitch length ratio of at least four to one.

9. An endless cutting chain as specified in claim 7 wherein at leastsome of said bit blocks extend upwardly from said body portion and theheight of said members is less than the height of said bit blocks.

10. In an endless cutting chain as specified in claim 7 wherein saidvolume has a conveying rate greater than the loose volume of minedmineral produced by said orbital movement of said links in a beddeddeposit 0 mineral.

1. A cutting chain comprising, a plurality of chain sections pivotallyconnected by parallel hinge pins to form a continuous chain of adjacentones of said sections, having a transverse width to pitch length ratiogreater than four to one, bit blocks carried by at least some of saidsections; and said sections having maTerial receiving portions forconveying material cut during movement of said continuous chain in abedded deposit of material. CM,2Ting chain as specified in claim 1wherein said conveying is at a rate greater than the loose volume rateof mineral production by said movement of said chain sections in abedded deposit of mineral.
 3. A cutting chain as specified in claim 1wherein each of said chain sections connects two of said pins at aplurality of points spaced longitudinally of said pins and each of saidpins extends the full width of said chain.
 4. A cutting chain asspecified in claim 1 wherein each of said chain sections has a pluralityof conveying means spaced along said hinge pins to form said materialreceiving portions.
 5. A cutting chain as specified in claim 4 whereinat least some of said bit blocks extend upwardly from said body portionand the height of said conveying means less than the height of said bitblocks.
 6. In a cutting chain as specified in claim 4 the furtherimprovement wherein said conveying means are located on interfittingportions of substantially continuous hinges.
 7. An endless cutting chaincomprising: a plurality of links, each of said links including a bodyportion having a transverse width greater than the length thereof, eachof said body portions being hingedly connected to adjacent ones of saidbody portions along axes extending in the direction of said width,respectively; bit blocks carried by at least some of said links; each ofsaid links having a plurality of members extending upwardly from saidbody portion and in said direction of said width, said members on aplurality of said links forming conveyor means extending substantiallycontinuously in said direction of said width, respectively, and adjacentpairs of said conveyor means spaced laterally from each other to formmaterial receiving portions of a volume to convey material cut duringorbital movement of said links in a bedded deposit of material.
 8. Anendless cutting chain as specified in claim 7 wherein adjacent linkshave a width to pitch length ratio of at least four to one.
 9. Anendless cutting chain as specified in claim 7 wherein at least some ofsaid bit blocks extend upwardly from said body portion and the height ofsaid members is less than the height of said bit blocks.
 10. In anendless cutting chain as specified in claim 7 wherein said volume has aconveying rate greater than the loose volume of mined mineral producedby said orbital movement of said links in a bedded deposit of mineral.